DE3405774A1 - Device for the simultaneous control of a fluid stream and measuring of a value proportional to the fluid stream and a second variable - Google Patents

Abstract

The device for the simultaneous control of a fluid stream and measuring of a value proportional to the fluid stream and a second variable is used particularly for measuring amounts of energy or heat, which are given off in a heater (107) of a heating installation, in order thus to, firstly, control and, secondly, measure, the heat emission of the heater (107). To this end, a volume flow regulator (1, 6, 16) and a valve unit (61, 62, 63), which is controlled by an external physical variable such as the room temperature desired, for closing off and permitting passage of the fluid stream, as well as an electronic unit (78, 112, 117), firstly for controlling the valve unit (61) and secondly and especially for carrying out and evaluating the measurement of the amount of energy or heat, are provided, the volume flow regulator (1) being designed as a multi-stage diaphragm regulator having at least one regulating and one compensation stage (6, 16) and being arranged with the valve unit (61, 21, 63) in series in a common through-flow housing (102) for the fluid stream. <IMAGE>

Description

Device for jointly controlling a fluid flow and measuring a the fluid flow and a second variable proportional value

The invention relates to a device for jointly controlling a Fluid flow and measurement of a value proportional to the fluid flow and a second physical variable, in particular for measuring energy and heat quantities, as with a radiator in a heating system for heating cost accounting, with a volume flow controller and a valve unit controlled by an external physical variable for blocking and Letting the fluid flow through and an electronics unit, in particular for carrying out and evaluating energy quantity measurements.

Such a device is in EP-OS 0018 566 (application number 80 102 118.9). The known device solves for the first time the task of controlling the fluid flow and simultaneously measuring the output of heat or energy, but is still too imprecise and complex, in particular in terms of production technology and installation, as well as not reliable in operation. But above all it is in the

Practice, in dirty heating water, not functional long enough. In addition, it requires high pump pressures and tends to produce impermissible flow noises and rattle. These previous serious disadvantages are closely related to the presence of sliding control parts, which can become dirty and jammed in the fluid flow.

The invention is therefore based on the object mentioned at the beginning To create a device that works better in practice, which is above all insensitive to dirt, long-term stable, accurate and reliable.

According to the invention, the stated object is achieved in a device of The type mentioned at the outset is achieved in that the volume flow regulator is a multi-stage membrane regulator with at least one control stage and one compensation stage, which each have a membrane, is formed, wherein the volume flow regulator and the valve unit one behind the other in one common flow housing are arranged for the fluid flow. According to the invention, there are initially no sliding control parts in the fluid flow used. The invention provides a compact device that can be accommodated in a common housing that is integrated in In this way, both the measurement of amounts of energy and volume variables and, on the other hand, the regulation or control of the reference variable with regard to it to a certain setpoint. The device controls and records with simple mechanics and electronics the amount of energy that is issued by an individual consumer. The device according to the invention can be used for various fields of application use is not limited to use in heating cost accounting or distribution. The device can, rather for example also for dosing, calibrated energy measurements, comparison unit measurements, as a control actuator part in heating technology etc. can be used.

According to a preferred embodiment it is provided that in the common Flow housing directly a flow detector to the valves Output of a signal indicating the flow state is assigned to the electronics unit. This configuration of a flow detector, too supports the goal specified with the task. The flow detector reports to the electronics unit whether there is a flow or not, because only in times of flow, for example, the different Temperature in a flow and a return to a radiator is used to calculate the heat emitted. To adapt to individual, different heating consumers, especially radiators, it is also provided that the flow rate allowed through by the volume flow controller is adjustable, the set flow rate of the fluid in the electronics unit if necessary. in coded form is taken into account when performing the energy measurement, whereby the Consideration can be done in various ways.

A further development provides that the control of the fluid flow and thus an amount of energy or heat carried along by this for at least partial delivery of the same in a radiator or the like. with fixed, by the volume flow regulator certain flow rate in the open state of the valve unit via a with a control part the adjustable thermostat connected to the energy unit by opening it and closing of the valve unit takes place, the reference variable or the setpoint value of the thermostat continuing over time in accordance with the predetermined values Values can be changed automatically. For this purpose, for example, various Ab I can be preprogrammed on program me, which the user selects or it can be provided by the user via one provided in the electronics unit Microprocessor its own Ab I can be compiled from a partial program on a program. The device according to the invention required because especially for switching the valve unit with regard to locking or the flowing through of the fluid, but also to regulate the constant

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Flow rates of the fluid, the inherent energy of the fluid is used and only additional energy to trigger a control pulse only little energy is required to switch over the valve unit. As a mechanical actuating impulse, this is normally generated by the expansion a thermostat cartridge. As an electrical control impulse In principle, this small amount of energy can also be obtained from the power grid. However, in order to avoid significant installation costs According to the preferred embodiment, only a small auxiliary battery is used. However, it is also possible to use solar cells with energy storage devices or semiconductor thermocouples (Peltier elements) for the energy supply. to be provided for converting the energy stored in the fluid flow into electrical energy.

Further advantages and features of the invention emerge from the claims and from the following description, in which exemplary embodiments of the device according to the invention are made with reference to FIG Drawings are explained in detail. It shows:

Figure 1 is an exterior view of a concrete

Embodiment of the device according to the invention;

Figure 2 shows the installation or arrangement of a

device according to the invention on a radiator;

Figure 3 is a block diagram of the invention

Contraption;

Figure 4 is a schematic representation of the

device according to the invention

Figure 5 is a longitudinal section through a concrete

Embodiment of the flow-through housing of a device according to the invention;

*
Figure 6 shows the representation of a magnet system and

FIG. 7 shows the illustration of a snap spring device.

The device according to the invention consists of a compact unit 101 with a flow housing 102 through which the fluid flow flows and in which the mechanical parts, in particular valve elements and electromagnetic Parts of the device according to the invention are housed. Furthermore, the unit 101 has a housing part 103 in which the electronics, the Display and the setting or default elements are housed. At the Flow housings 102 are two connections 104 for inlet and outlet (Only the outlet in Fig. 1 can be seen) is provided, by means of which the device according to the invention in the illustrated embodiment in the front I on line 106 to the radiator 107 of a heating system just as a conventional valve can be used (Fig. 2). A line 108 is provided on the unit 101, at the end of which there is a electrical temperature sensor 109, for example in a clamp or the like. is housed, which can be attached to the return line 111 from the heater 107 is. Another temperature sensor is accommodated in the housing 102 (not shown in detail) by means of which the flow temperature in the line 106 to the heating element 107 can be measured directly can. Different types of temperature sensors can be used, such as resistance thermometers, thermocouples or preferably electronic ones Current sensors which emit a current signal proportional to the absolute temperature and which can be connected in series so that

directly on the temperature difference between flow and return (106, 111) proportional current signal arises. If necessary, by means of active Thermocouples (Peltier elements), possibly using a Buffer accumulator the energy for the electronics of the device according to the invention from the (thermal) energy of the fluid flow to be measured can be obtained in a known manner.

The housing part 103 accommodating the electronics has a display 112 by means of which the energy consumed in or emitted by the heating element 107 can be displayed and read, for example in comparison units. Furthermore, a setting device 113 of a thermostat is provided, by means of which the target room temperature or the sequence of the target temperature can be set or preselected over time. A room temperature sensor 114 is integrated into the housing part 103, which measures the actual temperature of the room, which is compared with the current setpoint temperature for regulating the flow through the flow housing 102 to the heating element 107. In addition to the setting device 113 integrated in the housing part, a remote setpoint setting 113 ¹ and / or a remote sensor 114 ′ can also be provided, as is sketched in FIG.

FIG. 3 now shows a block diagram of the device according to the invention 101 shown. In the flow 106 to the heater 107 is first in the common flow housing 102 for the fluid in the illustrated Embodiment the valve 61 for blocking and letting the fluid flow through arranged, the valve system 61 having a main valve 62 and a control part 63. The control part 63 is controlled by a control device 78 depending on a comparison made in this between the current reference variable or the current setpoint, which is set via the setting device 113, and the actual value from

Room temperature sensor 114 controlled. Instead of adjusting device 113 and room temperature sensor 114, another control pulse can also be entered, e.g. from a time program. The switching of the fluid flow in detail takes place in the manner explained below. In the valve system 61 is followed by the volume flow controller 1, which after setting via an adjustable throttle by means of a control stage 6 and a downstream Compensation stage or cascade 16 an always constant amount or volume flow to the outlet 3 and thus to the radiator lets through.

A flow indicator 58 is also provided in the flow housing 102, which determines whether through the flow line 106 a through the volume flow controller regulated fluid flow takes place, or the fluid flow through the valve system 61 is interrupted. The measured by the flow detector 58 Information is passed on to the electronics unit 117 in the housing part 103. The same applies to the temperature measured with the Temper turf üh learners 109 and 118 in the return (111) - or before I to reitung (106) to Radiator 107. The information obtained in this way is then taken into account, taking into account the throttle setting, i.e. the given flow rate, processed in the electronic unit 117, for example, in coded form. The result or the summation of the measurements is then displayed via the display 112. Overall, by the invention Device 101 thus detects the amount of energy that is emitted by an individual consumer, here the heater 107, with the The amount of energy to be delivered is regulated or controlled in a predetermined manner via the controller 116.

The mechanical housed together in the flow housing 102 and electromagnetic control units are initially shown in FIG shown schematically.

The valve unit 61 for blocking and letting through a flow of liquid in a heating system has a main valve 62 and a control part 63 with a control valve, which is only shown in principle in FIG. The main valve 62 has a membrane 64 which is fixed with its peripheral edge in the wall of an outer housing or an insert part (both not shown in FIG. 4). The membrane 64 is elastic only in an annular area of the flexing zone M (FIG. 5) and is therefore actually designed as a membrane and has a rigid, plate-shaped valve cover 71 in its central area of the support zone. The valve cover 71 is assigned an annular valve seat 72 on the side of the membrane 64 facing an inlet 49, or this valve seat 72 lies opposite the valve cover 71. The valve cover 71 is pressed against the valve seat 72 by a spring or spiral spring 73. When the valve cover 71 rests on the valve seat 72, the main valve 62 is closed and there is no fluid flow from the inlet 2 to an outlet 2 ¹ to the volume flow regulator 1.

A bypass or a secondary line or connection 52 is led from the inlet 2 to a space 55 on the side of the membrane 64 facing away from the valve seat 72. In the same way, a secondary line 54 leads from the space 55 to the outlet 2 ^1. In the secondary line 54, which can be designed as a passage through the valve cover 71 (further below), a diaphragm opening 65 is arranged, which is preceded by a filter 66 . The control part 63 located in the secondary line 54 has a valve by means of which the secondary line 54 from the space 55 to the outlet 2 'can be opened or closed. The injector-like connection 67 of the connecting or secondary line 54 to the outlet 2 ¹ is such that when a liquid flows from the inlet 2 through the main valve 62 to the outlet 2 ¹ in the secondary line 54 is entrained according to the injector principle and thus in the line 54 and when the control part 63 is open in the space 55, a negative pressure is generated.

Let the valve unit 61 and thus in particular the main valve 62 now be closed. ^{There is a pressure P1 1} upstream of the main valve 62 and a pressure P1 at outlet 2 'which is lower than the pressure PV. In this closed state, control value 1.63 is also closed. The pressure P1 ″ in the space 55 has therefore ^{adjusted to the pressure P1 1} in the inlet 2 via the orifice 65. On the side of the membrane 64 facing away from the valve seat 72, the pressure P1 ^{1 ″ acts on it in addition to the spring force 73} The side of the diaphragm 64 facing the valve seat 72 acts on corresponding partial areas of the diaphragm. Since P1 is the lowest pressure of the valve unit 61, the forces acting on the diaphragm 64 from the space 55 are always higher than those from the side of the valve seat 72 so that the valve remains closed in this case.

If the control part 63 with the control valve is opened by a control pulse, the control valve itself and the opening process being explained in detail below, the pressure P1 ″ in the chamber 55 drops and closes with the lowest possible pressure drop to the pressure P1 at the outlet Due to the opening 65 with a smaller cross-section than at the passage 76 (FIG. 5), the chamber 55 cannot be filled up sufficiently quickly via the secondary line 52, so that a pressure difference between the inlet 2 with the pressure PV and the chamber 55 with the pressure PV '. Even with a small pressure difference PV-PV', the pressure PV can push the valve cover 71 off the valve seat 72 and thus open the main valve 62. Through the injector-like connection of the secondary line 54 to the outlet 2 ^{1 it} can also be achieved that the pressure P1 ″ in the space 55 is less than the pressure P1 at the outlet 2 ', so that even after the main valve 62 has been opened, it is reliably open n remains or is kept open. To close the valve system 61 and thus to interrupt a flow of liquid from inlet 2 to outlet 2 '

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the control valve of the control part 63 is closed by an impulse. A dynamic pressure occurs in the chamber 55 as a result of the initially existing pressure difference between the inlet 2 with the pressure PV and the lower pressure P1 ¹ 'in the chamber 55, so that over the opening 65 the pressure P1 "in the chamber 55 approaches the pressure P1 'until the forces of the pressure P1 "in the chamber 55 and the spring 73 outweigh the opposing forces of the pressures PV at inlet 2 and P 1 at outlet 2 on the diaphragm 64 and the main valve is thus closed is, as already mentioned above. The spring 73 already causes a differential force, even when there is no flow. In addition, the spring 73 prevents the diaphragm 64 from vibrating.

In the embodiment shown, the flow indicator is accommodated in the valve system 61 as a contactless or proximity switch for blocking or letting the fluid flow through, with which it is established whether or not there is a fluid flow at all. For this purpose, in the embodiment shown, a so-called reed switch 56 is arranged above the valve membrane 64. In the center of the membrane 64 or this membrane cover, a permanent magnet 57 is inserted, which, due to the change in its distance from the reed switch 56, switches the reed switch 56 with the movement of the membrane 64. The outlet 2 'of the valve system 61 leads as inlet 2 ¹ to the volume flow regulator 1 with its control stage 6 and a compensation stage or cascade 16. When the valve system 61 is open, from inlet 2 or inlet 2 ^{1 of} the volume flow regulator 1 to outlet 3 regardless of the pressure difference between Inlet and outlet a constant flow takes place !. The inlet 2 'leads to one side of the diaphragm 4 of the diaphragm valve referred to as control stage 6. The membrane 4 is thus acted upon on the side facing the inlet with the pressure P1 prevailing there.

A branch line 7 leads via an adjustable throttle 8, which controls the pressure P1 reduced to a pressure P2, to the other side of the membrane 4 of the control stage 6.

The control stage 6 initially has an essentially flat membrane 4 which is fixed with its peripheral edge in the wall of a cartridge 9 which can be inserted into an outer housing (not shown here). The membrane 4 is only elastic in a ring area and thus actually designed as a membrane, has a rigid, column-shaped valve cover 11. The valve cover 11 is on the Inlet 2 'facing away from the membrane 4, an annular valve seat assigned or is the valve cover 11 opposite. The valve seat 12 is firmly connected to the cartridge 9. The valve seat 12 encloses only a small area of the total area surrounding the cartridge. The valve cover 11 is pushed away from the valve seat 12 by a spring 13 which is supported on the valve seat 12. The variable passage between Valve cover 11 and valve seat 12 acts as a variable throttle, so that a space enclosed by valve seat 12 occurs In general, the pressure P3 is lower than the pressure P2. So prevail on the side of the membrane facing away from the inflow the pressures P2 and P3 as well as the areas assigned to them determine forces. The control stage 6 is another designated as cascade 16 Diaphragm valve arranged in series. It should be noted here that, even if in the sketchy illustration of FIG. 4 the cascade as well as the control stage 6 is shown, its dimensions as a rule can deviate from those of control level 6. Like the control stage 6, the cascade has a membrane 14 with a membrane cover 21, to which a valve seat 22 is assigned, from which the diaphragm cover 21 is pushed away by a spring 23 under corresponding pressure conditions will. The space facing away from the spring 23 and the valve seat 22

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of the valve 16 is directly with the space on that of their spring 12 and their Valve seat facing side of the membrane 4 connected, in which the pressure P2 prevails, so that in the aforementioned space of the cascade 16 also the pressure P2 prevails. From the inside of the valve seat 12, which is annular in cross section, a connection 17 leads to the valve seat 22 of the Cascade 16 surrounding space on the valve seat 22 facing side of the membrane 14, so that in this outer space the same pressure as inside of the valve seat 12, so P3 prevails. The control valve 6 thus acts as a variable throttle for the cascade 16 in accordance with the adjustable throttle Throttle 8 for control stage 6. At outlet 3 of the volume flow controller 1 then in the illustrated embodiment, the same pressure P4 prevails, as within the valve seat 22, if not between outlet 3 and Valve seat 22 further adjustable throttles or further ones of the cascades 16 corresponding cascades are arranged. The adjustable throttle 8 can consist of a fixed diaphragm part, which is displaceable against a Aperture part can be moved so that they together form a variable aperture opening, which is preferably sharp-edged is executed. Essentially round boundaries of the diaphragm opening are particularly advantageous, which are particularly advantageous in the case of small diaphragm openings Form an opening that is as circular as possible, i.e. a large area with a small and round perimeter. The resulting smallest aperture can e.g. become semi-circular and semi-square. Due to the sharp-edged and as circular as possible design of the aperture there will be a change in the aperture area as a result of soiling prevented. Instead of the displaceable throttle, however, replaceable circular insert panels can also be provided will. This makes it possible to use only one type of controller and different ones Insert panels to keep a large assortment of volume flow controllers with different flow rates in stock.

Reference is made to FIG. 5 below. In the figure 5 is a compact embodiment of the device according to the invention with volume flow controller 1 and integrated bistable open-close valve system shown in longitudinal section. The entire unit is accommodated in an outer housing 31 which has a connection piece 32 for the inlet 2 and a connection piece 33 for the outlet 3. The valve arrangements 6, 16 of the volume flow regulator 1 as well as the valve system are arranged in the cartridge 9 inserted in the housing 31.

The inlet 2 here leads to a chamber 34. Opposite the inlet 2 the membrane 4 of the membrane valve 6 is arranged. The membrane 4 is with its circumference firmly clamped in the cartridge 9, while its central part is designed as a rigid valve cover 11. On the the The side of the valve cover 11 facing away from the chamber 34 is provided with the valve seat 12, which is also fixedly arranged in the cartridge 9. The valve seat 12 is designed in the shape of a truncated cone, whereby it extends to the valve cover 11 tapers. As a result, the spring 13 can rest on the widest part of the valve seat 12 without the danger of its movement contact in the intermediate area on the valve seat could be prevented. The spring 13 presses with its side remote from the valve seat 12 against the valve cover 11 and therefore keeps the valve open in the depressurized state. The chamber 34 is connected via openings not shown in detail with a lateral Karnmer 36 in such a way that in the chamber 36 of the the same pressure P1 as in the chamber 34 prevails. The chamber 36 is about the by means of a handle 37 externally adjustable throttle 8 fluidly connected to a ring chamber 38 surrounding the valve seat 12, in which a the pressure P2 is lower than the pressure P1. Depending on the opening

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degree of the valve 6 due to the prevailing pressure conditions prevails in that through the valve seat 12 opposite the annular chamber 38 delimited interior 39 of the valve seat 12 a in general compared to the pressure P2 lower pressure P3. The further diaphragm valve 16 is arranged directly above the diaphragm valve 6, wherein a compact one due to the design of the valves as diaphragm valves Arrangement with a low overall height is achieved. The diaphragm valve 16 has the diaphragm 14, which also has on its outer edge the cartridge 9 is clamped firmly connected parts and has the valve cover 21 in its central area. The membrane 14 separates one Chamber 44 of an annular chamber 48, which surrounds a valve seat 22, which is also of truncated cone shape, at least over a partial area, which encloses an interior space 49. The outside of the valve seat 22 serves in a corresponding manner as an abutment for the spring 23, which rests with its other end on the valve cover 21 and this when pressureless Relationships from the valve seat 22 pushes away.

The chamber 44 is connected to the annular chamber 38 via passages 51, while the interior 39 of the valve seat 12 with the annular chamber 48 is connected above the membrane 14 via connection areas 50. The interior space delimited from the annular chamber 48 by the valve seat 22 49, which has a lower pressure P4 than the pressure P3 in the annular chamber 48, is via the open-close valve system 61 and above spaces located outside the cartridge, in particular between the outer wall of the cartridge and the inside of the wall of the housing 31 connected to the outlet 3 of the housing 31. In the invention The volume flow controller is also integrated here with the contactless or proximity switch 58 as a flow indicator. For this purpose is below the valve cover the reed switch 56 is arranged. In the center of the valve cover 11 is the Permanent magnet 57 used, which due to the change in its proximity to

Reed switch 56 with the movement of the valve cover 11 the reed switch 56 switches.

The entire valve unit 61 is also in the common housing 31 housed. The inlet space 49 is surrounded by the valve seat 72, which in turn is surrounded by part of the outlet 53 in the form of an annular channel is. The membrane 64 with the valve cover is located above the valve seat 72 71 arranged. It is pressed against the valve seat 72 by the spring 73. It can be seen in particular from FIG. 5 that the secondary line 52 from the inlet 49 to the chamber 55 is arranged in the valve cover 71 Has opening 65, the opening 65, the filter 66 being connected upstream. From the chamber 55 a narrow passage 76 leads to the secondary line 54 of the 4, which in the specific embodiment of FIG. 5 initially as a further chamber 54 and then in front of the injector connection 67 as an annular chamber is trained.

The control part 63 with a control valve 77, to which the passage 76 is now designed according to the invention as follows. The control valve 63 initially has a control device 78 from which control pulses Y, for example, by temperature change or exceeding or falling below certain temperature limits or due to other signals, a preferably bistable magnet system 79 is acted upon. A valve piston 81 is moved by the bistable magnet system 79 via an armature 82 attached to it in such a way that the passage 76 is either closed or opened. If the plunger 81 is in its lower position, shown in dashed lines, the passage 76 and so that the control valve 77 is closed, if the plunger 81 with the armature 82 is in its upper position, the passage 76 and thus the control valve 77 is opened. So that the magnet system has to take up as little energy as possible and this only for switching, but not for The plunger or plunger is used to hold the plunger 81 in the two positions

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81 here connected to an auxiliary spring 83, which is attached to its piston 81 opposite end is fixed on a bracket 84. The auxiliary spring 83 has the task of the control valve 77 in the closed state with a sufficient force (of a few grams) towards the valve seat press and hold tight. In principle, however, this function could also be fulfilled without an auxiliary spring, for example by a small one second permanent magnet at passage 76, one of which is ferromagnetic trained plunger 81 pulls on the valve seat. In principle then the control valve 77 or the plunger 81 is held in its two end positions (open and closed) each by a small permanent magnet and switched up or down by the magnetic pulses in both directions of the electromagnetic system. The auxiliary spring 83 could also be designed as a snap spring with two bistable positions, the open or closed position of the control valve 77 correspond. When the control valve 77 is in one of its two positions, So either the closed or the open position and in this position is held by the snap spring 83, the magnet system 79 only needs to switch the holding force of the Overcome spring 83. If the magnet system does this, the spring 83 snaps into its other bistable position and brings the control valve 77 into its other position, i.e. from the open to the closed position or but from the closed to the open position.

By the fact that the holding function of the valve 77 in either position guaranteed by auxiliary springs, snap springs or permanent magnets is, the magnet system 79 only needs energy to convert

switch, but not to hold control valve 77 in either or both Positions. The total energy consumption is so low that such a bistable heating valve with two cheap small auxiliary batteries size LR6 can be operated for a year.

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The switching of the entire valve system 61 takes place with reference in the manner described in FIG. 4, so that this need not be discussed further.

One embodiment of a bistable magnet system 79 is shown in the figure shown. The magnet system 79 has a magnetic circuit with a U-shaped yoke 86 and the movable armature 82, which with the Plunger 81 (Fig. 5) is connected. The web 87 of the yoke 86 is surrounded by the excitation coil 88 in the usual manner. While in particular the yoke consists of soft magnetic material, a permanent magnet 91 is inserted between the legs of the soft magnetic yoke 86. the magnetic field and force relationships are such that the permanent magnet 91 via the two legs 89 of the yoke 86 and the excitation coil 88 not switched on, the armature 82 in the position shown in FIG. 6 Hold the drawn tightened position securely, but no longer tighten from the position shown there with dashed lines.

Is now one of the one formed by the permanent magnet on the armature magnetic circuit counteracting magnetic field by switching on the When the excitation coil 88 is switched on, which acts as a displacement field with respect to the field of the permanent magnet, the armature falls at least from the yoke 89 from, wherein in an embodiment with an auxiliary spring, the displacement field the Permanent magnet field can overcome so far that the auxiliary spring 83 in their position corresponding to the closed position of the valve 77 is pressed will. In principle, however, it is sufficient that only the weight force is applied to the armature 82, for example, in addition to the various magnetic fields mentioned works.

Becomes a field that intensifies the permanent magnet field when switched on the excitation coil 88 is switched on, the armature from the dash-dotted line

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shown closed position in the shown drawn Open position (Fig. 6) pulled and possibly. the power of a snapper conventional spring and / or overcome the weight and the Armature in any case with the excitation coil 88 switched off in its upper, in Fig. 6 held position shown drawn. In order to strengthen the magnetic field, the legs 89 have a cross-sectional constriction 90 on.

It should be noted here that the bistable control part, for example, too may have magnetic and mechanical bistable parts or else a mechanical bistable element (snap spring) with a conventional magnet system or a bistable magnet system with unidirectional acting mechanical forces (usual spring, weight force), although the embodiments mentioned are preferred.

The illustrated mode of operation can be carried out by the illustrated bistable control part 63 of the valve system 61 can be carried out by only low switching energies are required for switching, which in the switching states but can be maintained without consuming any energy.

The bistable valve system can be actuated by various control pulses will. It can be used in addition to the described electrical on-off signal can also be switched mechanically by a mechanical variable, e.g. the displacement of a thermostat cartridge element. In this In this case, a snap spring device can be used instead of the magnet system 79 92, as shown in FIG. 7, can be used. A bistable snap spring 93, such as that used in Honeywell microswitches, is held here in a restraint 94. The movement of the snap spring is limited upwards by a stop 95 and downwards by the Control valve seat 80 at passage 76, on which the end of the snap spring attached tappet 81 rests when the valve is closed. The snap

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spring 93 is actuated by a transmission element 96 on which the expansion pin of a thermostat cartridge 97 acts. When the temperature rises, this thermostat cartridge 97 expands and presses on the Snap spring until it jumps into its closed position, i.e. it strikes the plunger 81 down onto the seat 80. When the thermostat cartridge cools down, its expansion pin pulls back upwards and the relieved one The snap spring jumps back into its open position against the upper stop 95. A play 98 is preferably provided on the plunger, of e.g. 0.3 mm, so that the snap spring initially has a certain initial energy when jumping into the other position as a result of this play reached before it has to pull the plunger with it. This enables a Actuation of the snap spring device 92 with minimal energy.

When used as a thermostatic valve in heating systems with one on the valve system 61 attached thermostat cartridge as a control device 78, temperature differences on the valve itself between the open state (with Heating water of e.g. 90 C) and closed state (when the heating water cools down to room temperature again) to different lead thermal expansions in the control valve 77, so that with the same setting of the control device 78 or the setpoint setting on the Thermostat cartridge when open and warm, another switching point at the snap spring 93, i.e. a different switching temperature results than when the cold valve is closed. This switching point difference can e.g. 0.5 - 1 ° C. By introducing a thermal expansion compensation element between cartridge 97 and control part 63 or snap spring 93 this switching difference can be varied, e.g. by appropriate

Design of the transmission element 96. This switching difference can can be made as small as possible, but it can also take on a desired size, so that e.g. when it is cold it is switched on 0.5 earlier than when the valve is warm. For this purpose, the thermal expansion compensation element is selected with regard to its dimensions and expansion coefficient so that

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that the difference between its thermal expansion and that of the surrounding bracket and thus also the switching point difference assumes a desired size between the warm and cold valve. For example, it can be the thermal expansion compensation element can be made as a transmission element 96 from polypropylene. This difference can also be influenced or can be set as required by the heat transfer from the valve to the thermostat cartridge through appropriately dosed insulation between valve and cartridge is influenced, e.g. by insulating material and vents.

The following are supplementary guidelines for the preferred design of the on-off valve system 61 given.

The aperture 65, also called the bore, should be selected to be as small as possible e.g. with a diameter of 0.5mm, preferably between 0.3 and 0.6mm, so that only very small amounts of liquid can flow through. The opening 65 must in no way be due to Dirt deposits become completely clogged. To do this, it is once circular and with sharp knife-like aperture edges, where no deposits can form. In addition, a fine filter 66 is connected upstream of the opening 65. This filter 66 has in proportion a large surface for the small amount of liquid flowing through so that it cannot become completely clogged due to contamination even after a very long time. Advantageously, this can Filters are divided into two zones, with one zone flowing through, the other not flowing through. A certain amount of Self-cleaning can be achieved by the flow, while in the no-flow zone as a result of almost vanishing flow velocity accordingly little contamination is carried on the filter. They don't The flow zone of the filter is preferably arranged at the top, so that heavy dirt particles can no longer be dragged along. Depending on the type of Soiling can then turn out to be one or the other of the two zones to be less susceptible to soiling. However, both zones are each like that great that they alone have a long-term sufficient flow for the small one

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Ensure nozzle 65. A filter arrangement can also be used for the filter 66 with many folds to increase the filter surface in a small volume to get voted. The filter is made of non-ferromagnetic material, e.g. plastic fabric or bronze. It can be very thin Be a sintered filter or a filter fabric. The pore size of the filter is preferably selected to be 5 to 10 times smaller than the filter opening.

The dimension of the passage 76 on the control valve 77 must be selected to be significantly larger than the opening 65, the diameter of the passage 76 is preferably between 1 and 2mm, e.g., an area ratio from passage 76 to aperture 65 from 5 to 10 arises.

From the foregoing it can be seen that while maintaining a compact Design the series arrangement of on-off valve systems and volume flow controller 1 can be interchanged as required. Likewise the flow sensor 54 can be arranged largely in any way.

The regulation of the flow of the fluid to and through the radiator 107 and keeping the flow rate constant when the open-close valve is open system 61 now happens as follows:

The setting device 113 is used to set a Sol I temperature value for the room, in which the heating element 107 is located or a program for the target temperature has been preselected. The actual value is then entered in the controller 78 the room temperature measured via the room temperature sensor 114 and compared with the setpoint. If the actual value changes via the momentary target value, the controller sends a switching pulse to the valve system 61, namely an opening pulse when the actual value drops below the target value and a closing pulse when the actual value rises above the SolI value.

340577A

Is now the main valve 62 of the valve system 61 by an actuating pulse opened by the controller 78 in a manner described above with reference to FIG. 4 and thus the path from the space 49 to the annular channel 53 (Fig. 5) released, the volume flow controller 1 works in the following way:

When the chamber 34 is depressurized because there is no liquid through the inlet is supplied, the diaphragm valve 6 is in its fully open position, since the diaphragm 4 is under the exclusive action of the spring is pushed away from the valve seat 12. In the operating state it builds up in front of the Volume flow controller a system pressure P1. After the volume flow controller there is a pressure P4, which is created by the working resistance at the consumer is determined. By changing work resistance and changing System pressure, the pressure gradient between P1 and P4 can change. The prerequisite for the constant flow is a constant Pressure drop at the adjustable reference throttle 8, whereby to achieve of the desired nominal flow rate, a minimum effective pressure or pressure threshold value is required. However, if the differential pressure is greater, the excess must Pressure can be destroyed by throttling in control stage 6 and the cascade so that the flow is within a low tolerance or Error range remains constant.

If there is no flow at the valve, it acts on the diaphragm 4 no pressure, the controllable throttle points 6, 16 are open. The membrane 4, 14 are moved by the springs 13, 23 from the corresponding valve seat 12, 22 pushed away. At the onset of a flow and increased system pressure P1 at the inlet 2, the membrane 4 is first of all further against the valve seat pressed. At the same time, liquid flows through the adjustable reference throttle 8 into the annular space 38, where a pressure P2 is established, and from this space into the interior 39 within the valve seat 12 via the valve openings between the valve cover 11 and valve seat 12, where a pressure P3 is then initially established. The by the pressures P2 and P3 on the Forces acting on the membrane 4 counteract the force caused by the pressure P1 until the membrane 4, which acts as a pressure compensator, adjusts itself in such a way that d £

the change in the pressure drop P2 - P3 corresponds to the change in P1 - P3 and thus the pressure drop P1 - P2 at the throttle setting remains approximately constant. The differential pressure P2 - P3, however, determines a disturbance factor, so that the pressure difference mentioned, if it is a the value exceeding the flow tolerances is reached, further reduced must become. The additional diaphragm valve or the cascade is used for this In this case, the reference pressure is variable because it differs from the previous one Control stage 6 has the differential pressure P2 - P 3 as the control basis. Which The pressure difference P3-P4 which is set via the valve 16 is then lower, so that a sufficient flow constancy can be achieved. In general, a cascade is sufficient. In special cases, additional Cascades can be arranged behind the cascade 16.

According to the invention, the two-stage or multi-stage arrangement of Diaphragm valves are a very precise, long-term stable, insensitive to contamination and a compact volume flow controller has been created that can work in a wide range of differential pressures. The adjustable Throttle 8, 37 the target flow rate can be selected.

To prevent any coarser contamination in the heating water at the inlet a replaceable filter, e.g. a bronze grille of 0.2mm Mesh size to be attached. Fine impurities do not impair the function of the volume flow controller.

The membranes 4, 14 are preferably designed to be essentially flat, i.e. they have a relatively small flexing zone M and a relatively large support surface (with valve cover) in between. Moreover, should the membranes have a very low intrinsic rigidity of preferably less have a membrane area of more than three grams / cm and a large stroke range. RoI! Membranes, beaded membranes or compressed membranes are particularly suitable for this Flat membranes. EPDM, for example, are suitable as a material and Viton with hardnesses of 55 - 70 ° Shore and thicknesses of for example

0.2-0.4mm. If high overpressures are to be expected, Any membranes affected by this can also be reinforced with a fabric insert.

The best results are achieved with the largest possible membrane surface, therefore the membrane diameter should preferably be at least 70% of the cartridge diameter or the inside diameter of the housing 31. The openings of the valve seats 12, 22 are intended on the one hand to achieve a high control accuracy should be relatively small and on the other hand, the flow resistance at the valve should not be too great. Good results can therefore be achieved if the valve diameter is between 35 and 45% of the diaphragm diameter.

In order to achieve the desired high flow rates and low threshold values of the To achieve differential pressure, the flow resistances should be kept small. For this purpose, given the housing diameter, the Dimensions of membrane and inlet and outlet channels kept large and the wall thicknesses including the wall thickness W for the clamping area of the Membrane kept small. For this purpose, instead of using a bead as shown in FIG. 5, the membrane can also be clamped directly in a thin wall W, glued in or vulcanized on. On the whole Strömingsweg with the exception of the necessary sharpness through the volume flow controller Fade the borders without edges and corners, be as smooth, round and continuous as possible. Instead of the concentric feed and Discharge channels 50 and 53 with the diameters V and R can also be divided radially, so that the channels 50 and 53 in the section of FIG. 5 not arranged next to one another, but one behind the other would be. The shape of the outer housing 31 can also be made square, in which case the corners that are not circular Membranes are covered, space is available for the channels and 53. With versions of the volume flow controller according to the explained

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constructive guidelines, the following very good results can e.g. for a 3/8 inch valve and standard connections the following can be achieved:

Threshold values of the differential pressure of less than 0.1 bar, volume flows of at least 200 l / h and Accuracies of 2% over a very wide effective pressure range up to pressures of over 1 bar.

Depending on the desired application, the construction can be according to the specified Guidelines are optimized.

When choosing the material, care should also be taken to ensure that the various Elements are electrochemically and chemically resident, i. that they do not react chemically in the fluid flow and in relation to the surrounding housing and lines. That e.g. the valve springs are in a brass housing 13 and 23 are made of spring bronze or acid-proof steel

Instead of the ring springs from FIG. 5, other springs such as leaf springs can also be used or torsion springs are used. Are especially beneficial also the compact disc springs, which have a low overall height of the housing and enable short connection channels. In principle, however, the spring can also be integrated into the membrane.

Depending on whether the flow detector 58 detects a flow or not, the temperature difference of the thermal sensors 109, 118 is measured and that in the electronic unit 117 with the coded setting of the flow rate multiplied through the throttle 8 and integrated over the time of the opening point of the valve sy stars 61 or summed up that the summed up Energy consumption can be displayed relative or in absolute values via the display 12 (FIG. 3). The electronic processing takes place for example using series-connected current sensors (such as LM 234), which then generates a current signal proportional to the temperature difference output, which is converted into pulses via a capacitor or via A / D-

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Converter is further processed and added up.

The device according to the invention allows that in a simple manner Form the product of two physical quantities and integrate them over time and thus to specify a consumption unit, which is given either as a comparison value or as a calibrated physical unit will. One physical quantity corresponds to the mass flow, which is kept constant by the volume flow controller 1, the flow rate being transmitted to the electronic unit 117 and after setting is included in the measurement as a constant volume flow rate. The second value is a process-dependent variable, for example a temperature difference measured by means of the thermal sensors 109, 118 different temperatures, a concentration or the like. Both sizes result in the consumer variable, for example the heat or amount of energy given off by the radiator 107 as a physical unit. Since the actuator in the control part 63 of the valve system 61 only consumes a small amount of energy, the regulation can be carried out by small, cheap ones Auxiliary batteries can be maintained for years. If the above The device according to the invention has been described with regard to the heating cost billing or distribution, so can with a corresponding Design of the device according to the invention, this also for dosing, calibrated energy measurements, comparison unit measurements, as a control actuator in general in heating technology, etc. are used.

The in the above description, in the drawing and in the Features of the invention disclosed in the claims can be used both individually and in suitable combinations for implementing the invention in their various embodiments may be essential.

- L eerseit ο

Claims (17)

; _ PATENT CLAIMS .y Device for jointly controlling a fluid flow and measuring a value proportional to the fluid flow and a second physical variable, in particular for measuring energy and heat quantities, as in a radiator of a heating system for thermostatic control and for heat consumption measurement with a volume flow controller and one from an external one Physical variable controlled valve unit for blocking and letting the fluid flow through as well as an electronic unit, in particular for carrying out and evaluating energy quantity measurements, characterized in that the volume flow regulator is a multi-stage membrane regulator with at least one control and one compensation stage (6, 16), each of which has a membrane (4, 14), the volume flow regulator (1) and the valve unit (61) being arranged one behind the other on a common throughflow housing (31, 102) for the fluid flow. 2. Apparatus according to claim 1, characterized in that a flow detector (58) for outputting a flow condition indicating signal to the electronic unit (117) is provided. 3. Device according to claim 1 or 2, characterized in that that the flow rate allowed by the volume flow controller (1,6, 16) can be adjusted by means of a throttle (8), wherein the set flow rate of the fluid in the electronic unit (117) if necessary compulsorily and in coded form when performing the energy measurement. 4. Device according to one of the. Claims 1 to 3, characterized in that that the regulation of the fluid flow and thus an amount of energy or heat carried through it at least partial delivery of the same in a radiator or the like with a fixed setting by the volume flow controller (1, 6, 16) certain flow rate in the open state of the valve unit (61) via a control device (78) of the electronics unit (117) connected adjustable thermostats (113, 114) takes place by opening and closing the valve unit (61). 5. Device according to claim 4, characterized in that the reference variable or the setpoint of the thermostat (113, 114) can be changed automatically over time according to specified values. 6. Device according to one of the preceding claims, characterized in that the energy supply or solar cells Semiconductor thermocouples (Peltier elements) for converting the energy stored in the fluid flow into electrical energy are provided. 7. Device according to one of the preceding claims, characterized in that the thermal sensor (109, 118) in each case in Vorbzw. The return from the radiator (107) is arranged and connected to a network of the electronic part (117) that integrates over time are connected, these thermal sensors being designed, for example, as series-connected current sensors. 8. The device according to claim 1, characterized in that for controlling the control part (63) of the valve unit (61) a time, a PH, a concentration, a level meter or a preprogrammed control sequence is used. 9. Device according to one of the preceding claims, characterized in that a pressure difference on both sides of the Diaphragm (4) of the diaphragm valve (6) causing throttle (8) adjustable and designed as a sharp aperture with a substantially round border. 10. Device according to one of the preceding claims, characterized in that the pressure difference at least at one of the diaphragm valves (16) by the one arranged in series in front of this Diaphragm control valve (6), which acts as a throttle, is formed. 11. The device according to claim 2, characterized in that the flow detector (58) as a membrane valve (6, 16, 62) associated contactless switch is formed, for example from a reed contact (56) on the housing and a permanent magnet (57) on a valve cover of the diaphragm valves existing. 12. Device according to one of the preceding claims, characterized in that the valve unit (61) each have a control part (63) and a main valve (62), the control value! a bistable actuator (79, 81,82,83,92) which no energy in its end positions and only one to switch over minimal energy required. 13. Apparatus according to claim 12, characterized in that the actuator comprises a mechanical bistable element such as a snap spring device (92). 14. The device according to claim 12, characterized in that the actuator has a bistable electromagnetic element, for example with a switchable electromagnet (79) and a permanent magnet (91). 15. Device according to one of the preceding claims, characterized characterized in that all valves (6, 16) of the volume flow regulator and a main valve (62) of the valve unit (61) as diaphragm valves, each with a diaphragm of low rigidity are formed, the membrane surface covering the cross section of the housing (31) for the most part. 16. Vonrichtung according to any one of the preceding claims, characterized characterized in that in the main valve (62) a diaphragm-like Opening (65) to ensure a secondary line (52, 54, 55) for the Z weig of the control part (63) is formed; being this Opening (65) is preceded by a filter (66). 17. Device according to one of the preceding claims, characterized in that the control part (63) is a thermal expansion compensation element (96).